Feeder for carton blanks



July 28, 1953 E. J. PAGENDARM FEEDER FOR CARTON BLANKS Filed Jan. 28, 1947 FllE| -J 5 Sheets-Sheet l mv ENTOR [dwara'J Page/7 dar'm ATTO RN Ev July 28, 1953 E. J. PAGENDARM 2,646,983

FEEDER FOR CARTON BLANKS Filed Jan. 28, 1947 5 Sheets-Sheet 5 uvwzzvrox. fawar'oJ Payendarm ATTORNE Y Patented July 28, 1953 UNITED STATES FEEDER FOR CARTON BLANKS Edward J. Pagendarm, San Mateo, Calif., assignor to Bemiss-Jason Company, a corporation of California Application January 28, 1947, Serial No. 724,762

5 Claims.

This invention relates to improvements in the art of box manufacture and particularly to a machine useful in the conversion of a flat blank into a container.

It is usual in the box art to form a series of similar blanks by cutting a continuous sheet of a suitable stock, the blanks so formed being transported in stacks to a consumers place of business and there assembled to provide the container or box. If the containers are assembled by machine, the several elements are usually secured together by application of an adhesive.

In the Meller Patents 2,366,419 and 2,404,916 and in Patents 2,528,900 and 2,550,582, a folding box is disclosed wherein, in general terms, one

or more corners are provided by planar panels hingedly supported for positioning in a face-toface engagement and in which position the planar panels are secured by a cut face or edge on one panel engaging cooperatively a cut face or edge on the other panel in looking engagement such as may be provided by a face-to-face engagement, maintained, within the compression strength limit of the blank, as by a threading of one panel portion through a portion of the cut in the other panel so that the one is drawn or flexed, at least in part, into the plane of the other panel in locking engagement with the other panel. Boxes, containers and the preformed blanks therefor, within the above definition, such as those disclosed by Meller, will, for convenience, be sometimes referred to herein as being of the interlocking dual planar panel type. The blanks are usually formed by cutting a suitable stock to the size and shape desired, a fiat, cut blank resulting.

The interlocking dual planar panel type of container is capable of assembly by the cooperating action of a support for the blank, such as a plunger, and a die through which the blank support is passed, the panels being moved, as the blank is passed through the die, into a face-toface relationship.

It should be obvious that the manipulative steps are relatively simple, as compared to the assembly of a glued container, and that these steps can be performed rapidly. Since an adhesive it not required, the speed of assembly is independent of various factors inherent in the use of such a material and, for this reason, the assembly rate can be varied over a wide range. This enables blanks of the dual planar panel type to be assembled rapidly and at a rate 00- ordinated directly with the demand even though this varies over a relatively wide range whereas a glue machine must operate at a substantially constant rate and this relatively low.

The machine of the present invention is capable of receiving a stack of preformed blanks and of rapidly converting these, in succession,

into boxes or containers. The only hand operation required is the placement, from time to time, of a fresh stack of blanks in position for feeding. The assembly of the blank into a container is quickly effected and at widely varying rates of production so that the container production rate can be suited to the container demand rate.

The machine of the present invention includes a support wherein a stack of preformed blanks is placed on edge and in face-to-face abutment. The foremost blank is fed in a positive manner to the means provided for converting the blank into a container or box. The feeding means is such that each blank is fed positively into final position so that feeding errors are minimized, if not completely obviated, and so that a relatively high rate of blank conversion can be established and maintained.

The machine to be described is particularly suited to the feeding and the assembly of a blank to produce a container of the dual planar panel type and, for this reason, it will be described in this connection so that one mode of specific application of the invention will be made apparent.

It is in general the broad object of the present invention to provide a machine for receiving a stack of preformed blanks of the interlocking dual planar panel type and for converting these, one after the other, into a box or container.

Another object of the invention is to provide an improved and novel positive feeder device for removing the foremost paper sheet blank in a stack and delivering it rapidly and positively for interlocking at least two panels of the blank to form a container corner.

The invention includes other objects and features of advantage, some of which, together with the foregoing, will appear hereinafter wherein the present preferred form of machine is disclosed.

Referring to the drawings accompanying and forming a part hereof, Figure 1 is a side elevation of the right-hand side of the machine.

Figure 2 is a side elevation of the left-hand side of the machine.

Figure 3 is a section taken vertically through the machine along the line 3-3 in Figure 5.

Figure 4 is a section taken along the line 4-4 in Figure 3.

Figure 5 is a section taken along the line 5-5 in Figure 1.

Figure 6 is a view taken along the line 6-45 in Figure 5, illustrating the construction of the clutch.

Figure 7 is a section through the clutch taken along the line 11 in Figure 6.

Figure 'l-A is a section taken through the clutch mechanism between the sprocket 203 and the hub of ratchet wheel 2l6.

Figure 8 is a fragmentary side elevation, partly in section, illustrating the cam utilized to operate a portion of the blank delivery mechanism, the view being particularly a section taken along the line 8-8 of Figure 5.

Figure 9 is a side elevation, partly in section, of a modified form of a positive blank feeder.

Figure 10 is a plan view, with portions of the structure broken away, of the feeder shown in Figure 9.

Figure 11 is a section taken along the line 2l2| in Figure 10.

The frame Referring to the drawings, the machine of the present invention includes a suitable frame, generally indicated by numeral El, and comprising a right side frame 22 (Figure 1) and a left side frame 23 (Figure 2), the two being joined together by suitable generally horizontal frame members 2 3 (Figure 3). Each side frame includes members 26 and 2'1 extending in a generally vertical direction at each end of the frame and joined together, adjacent their floor or ground ends, by horizontal frame members 28 and, at their upper ends, by a frame member 29 which extends at an acute angle to the horizontal. Intermediate frame members 3| and 32 extend between frame members 28 and 29. The members 32 in side frames 22 and 23 are joined together by transverse member 33 while subframe members 34 and 36 extend between the transverse frame member 33 and one of the transverse frame members 2 1 to provide a support for presently described power transmission and drive mechanism.

Any suitable frame construction can be utilized and that which I have specifically described is the one which I have successfully utilized in conjunction with the other machine components to be presently described.

The drive The details of the machine construction may be more conveniently understood by considering the drive mechanism provided and by tracing through the force application made to some of the elements of the macihne to the end that the plunger and die mechanisms 93 and 94 can be moved with respect to one another in the correct time relationships and a blank can be delivered positively to these at the correct time in their movement with respect to each other.

A suitable prime mover, such as an electric motor 4|, is mounted upon frame 25, the motor including a V-belt pulley 42 on its drive shaft .3. A V-belt 44 is trained about the pulley 42 and about an adjustable sheave in a speed change device generally indicated by numeral 46 and which includes brackets 41 mounted upon bars 31 and supported by members 34 and 35. Links 38 are hinged upon bratckets M to provide a support for shaft 69 which carries two like outer single V-pulley elements 50 and an intermediate double V-pulley element (not shown) which cooperates with each of the pulley elements 50 to provide two V-shaped pulleys of variable size and which are complementary to one another. The other end of the link 48 is carried by a nut 51 mounted upon screw threaded rod 52 extending through the frame and having a crank handle 53 thereon. A V-belt is trained about the other variable sheave 58 in the speed change de- 'upon shafts H4 and H6.

vice 46 and about a large V-belt pulley 54 mounted for rotation upon shaft 55; shaft 56 (sometimes referred to hereinafter as the clutch shaft), is carried in suitable journals 51 mounted upon frame members 28 on each side of the machine. The speed of operation of the machine can then be varied simply and quickly by varying the speed change device with handle 53.

Secured to the V-belt pulley 54, for rotation therewith freely upon shaft 56, are chain sprockets 6i and 52. A chain 63 is trained about sprocket GI and about sprocket 6 3 mounted upon jack shaft 6'6; the jack shaft is carried in journals 67 which are mounted upon frame members 34 and 36. Pinion gear 68 on the jack shaft drives the gear 69 on crank shaft II; the crank shaft is carried in journals l2 which are mounted upon frame members 34 and 35. Crank arms E3, provided upon each end of the crank shaft, are connected by links I83 to the plunger mechanism 93 to reciprocate this.

To drive the mechanism for feeding the blanks, sprocket i6 is mounted upon the crank shaft H and chain TI is trained about this sprocket and about a sprocket 78 secured to the clutch shaft 56. In this connection, I again wish to point out that the large sheave 54 rotates freely upon clutch shaft 55 together with its associated sprockets 6i and 2. A chain 8| is trained about the other sprocket 62 and about a sprocket 82 on a shaft 83 which is carried in journals 84 mounted upon members 31 of the frame. At one end, shaft 33 carries a hand wheel 85; this is usually of considerable mass to provide for damping out of any unevenness in the drive due to the reciprocation of plunger 93 and, at the same time, to permit of the machine being turned over by hand for adjustment or to ascertain that the several units are operating in the correct relationship to one another and at the correct time in relation to one another. Shaft 83 is also utilized to drive other components which will be presently described.

General description of blank converting mechanism ings lfil. The links :53 are extended between each of the rods $3 and crank arms 53 mounted upon crank shaft 'il so that the plunger 93 is moved from above the die through the die and then back to above the die during each rotation of crank shaft ll.

During the plunger travel, a blank, suitably interposed between the plunger 93 and the die member at is converted to a desired locked-up container. The completed, locked-up container drops onto a suitable conveyor structure and is moved away to a point of use. The conveyor shown is provided by the several belts i ll (Figures 1, 3 and 5) and trained about pulleys H 2 and -I [3, the pulleys being respectively mounted Shaft H4 is carried in suitable journals Hi mounted upon the frame members I28 while shaft H6 is carried in suitable journals on brackets H8 on frame members 28. Shaft II4 is driven by a chain H8 trained about a sprocket I2I on clutch shaft 56 and about a sprocket I22 on shaft H4.

The blank feeding mechanism To feed each foremost blank in turn and in position to be formed into a completed structure, a suitable blank storage and feed mechanism I23 is provided. In the form illustrated in Figures 1-10, this comprises the frame members I24 secured on each side frame 22 and 23 and having a bottom provided by spaced plates I25 and an intermediate plate I26. The plates I25 are secured in position while plate I 26 is movable so it can be vibrated, as will be presently described. A slide member I21 is extended between the plates I25 adjacent to but adjustably spaced from a blank drive Wheel I 84 so that only the foremost blank is released and is fed from the stock; the adjustment is provided by an angle iron I28 secured between the frame members I24, and a screw I29 provided between these so that the slide I21 can be moved with respect to the wheel I84. The screw I29 is utilized to space the ends of slide I21 from the wheel I84 a distance just sufficient to permit the foremost blank to move from the stack and to drop into engagement with the belts 243 when the support provided by fingers I5I is momentarily withdrawn.

Across the rear of plates I25 a threaded rod I32 is extended, the rod being mounted for rotation in brackets I38 and having a crank I34 thereon. Threaded sleeves I33 are mounted on the rod to support adjustably the end or guide walls I35 for a supply of blanks.

The blanks are usually placed in the storage and feed mechanism on edge and in a nearly vertical position, being supported in this position by the bottom plates I25 and I28 and by wheels I8I on rotatable shaft I82 mounted in a pair of arms I 38 which are hinged on frame members I 24 with a rod I31 provided between the arms as a spacer and brace. The position of the wheels I8I with respect to the end of the bottom plates I25 and I21 and to the vertical can be adjusted by rotating the arms; this is accomplished by hand screw I4I which engages plate I42 on the frame members I24. The screw I4i extends through a nut I43 carried on a transverse member I44 which is secured to arms I45 rigid with the arms I35.

The structure so far described suffices to support the bulk of the blanks in a generally vertical position in which each blank is standing on edge and in a face-to-back engagement with those on either side except the foremost blank. Means are provided for feeding the foremost blank from the stack in a timed relationship to operation of the plunger and die mechanism. This means includes spaced fingers I5I carried adjustably upon shaft I 52, the shaft being extended between arms I53 which are pivoted as at I54 upon frame I24. A link I51 is suitably adjustably secured to the end of each arm I53 and extends to a lever I8I pivotally mounted upon each frame member 32 as at I82. Lever I6! carries a cam follower I83 riding along the surface of a cam I64 mounted upon the shaft I I4 which, as previously described, is continuously driven from clutch shaft 56 by a chain II9 extended about a sprocket I22 on one end of the shaft I I4.

The position of each cam I84 on the shaft II4 can be suitably altered to secure the correctly timed movement of fingers I5I sprocket I22 includes an arm I88 (Figure 8) extending therefrom and carrying a stud I61 extending into a suitable slot I68 in each cam I64. By loosening nut I69 on each stud, the relation of the cam, and particularly the dwell I1I therein, with respect to the shaft II4 can be suitably changed so that cam follower I83 drops into the dwell at the correct time interval to rock fingers I5I clockwise in Figure 3 and out of supporting engagement with the foremost blank.

The foremost carton blank in the stack support I23 rests upon the ends of fingers I5I and against rollers I8I on shaft I82 and between slide I21 and wheel I84, the weight of the other blanks in the stack holding the foremost blank against the feed wheel with a force sufficient to ensure the requisite frictional engagement of the foremost blank with the feed wheel. When the cam follower I83 drops into the dwell I1I on cam I64, fingers I5I are rocked clockwise in Figure 3 and the foremost blank is free of any support along its bottom edge. The blank is then moved positively from between the slide I21 and the wheel, past the fingers I5I and down into a position wherein the blank rests on pins 35I and in position between the die and the plunger. This positive drive means includes the rollers I8I on shaft I82 and positive drive wheel I84 on shaft I83. The drive wheel I84 has a suitable surface for positive driving engagement with the foremost blank such as may be provided by sponge rubber 184a.

The positive drive by wheel I 84 is facilitated by fingers I5I moving counterclockwise (Figure 3) as soon as they have released the foremost blank so that they rest against the released blank and provide a support for the new foremost blank in feeding position so that the new foremost blank cannot follow the blank which has just been released and is being fed on to the plunger and die.

To ensure that the foremost blank drops freely when released from the wheel I84 and that the other blanks move into position, means are provided for vibrating rapidly the intermediate plate I26. This means includes a shaft I81 mounted upon suitable brackets I88 on frame members I24 and an eccentric I88 provided thereon to oscillate the plate I26. The eccentric engages a roller I12 carried on a lever I13 hinged between bracket I14 on plates I25. The lever rides against an adjustable stop I15 on plate I26 to vibrate this as the eccentric is rotated.

To drive roller shaft I82, drive wheel shaft I83 and vibrator shaft I81, a V-belt pulley I9I, I92, I93 is provided on each of the shafts and a V-belt I94 is trained about the several pulleys and is retained in engagement therewith by idler pulley I96 adjustably supported by adjustable lever I91. To drive the feed wheels or rollers I8I and I84 in the proper timed relationship and to operate the blank stock vibrator eccentric I88, a sprocket 2UI is provided upon one end of shaft I83. A chain 282 is extended about this sprocket and about a sprocket 283 on the clutch shaft 56.

It will be noted that the shafts I82, I83 and I81 are operated off a common shaft, the clutch shaft 58 by sprocket 203. The positive drive wheel I84 and the rollers I8I are preferably only driven intermittently during blank feeding to reduce abrasion and because the constant running of the wheel I84 may tend to buckle blanks of light weight stock. The drive of the blank feed wheel I84 is preferably such that the wheel starts; to

rotate just priorto release'of the foremost blank "so thatLby thetime the blank is releasedthewheel is moving at feeding speed. Rotation of -=the feed wheel is continued until the nextzblank-isengaged with fingers $51 so that the wheelis effective to 'move this blank into positive engagement with the fingers l! to avoid mis-alignment of the blank during feed to the plunger-anddie mechanism. Since the size of the blank fed avill vary with the commodity packaged, it is desirable to vary the extent of rotation of the wheel 1&4. This is accomplished by an adjustable positive -clutch=mechanism which is shown in :Figures 5,6, '7 and l-A. This mechanism includes sprocket 203 having a bushing 285 secured thereto and supporting thesprocket for free rotationonshaft 56. A ratchet wheel 2H3, having a hub 229, is mounted on bushing L205, the endof the .hub adjacentthe sprocket being notched asat22i to engage ears 22'lon thesprocket. Mounted-upon an end of the continuously rotating-shaft'fififis-a disc'ZGB. Supported. upon :the disc and rotatable therewith is -a bolt 209 carrying .a dog ZH, the dog having a cam follower 2l 2 =thereon; a spring 2I3, extended betweenpin 2i5 on the disc and the dog, biases the cam follower in against .the surface of acam 2M whichissecuredto-a fixed plate 285. The plate lite-extendsfroma support bracket 20101). frame member-23 on the left ha-nd side of the machine, the plate -Zil8havingears 228 which fit in-notches 229 (Figured-A) in hub 230 on the cam il i to-securethe latter against rotation. As the cam follower revolves around the cam-the follower t2 drops ratchettooth 2 l 3 into engagement with one of the teethon .the ratchet=-wheel-to rotate this and thesprocket for that: period-of 1 time during 1 which the 'tooth is in engagement with the ratchet wheel. Since the cam 2M is-fixed in-position with respecttothe sprocketgthe engagement of the ratchettoothiZ l 8 with the-ratchet wheels occurs at the samepoint in each cycle of operation.

To vary: the? length of I the period of engagement of the .ratchet tooth 2 l 8 with :the a ratchet wheel and, consequently the driving of the blank feed V -thereon, the :plate and cam' being rotatable :on

thehub itfl. Plate 22! is locked-impositionzby arm 2-3! which extendsfrom bracket 20'! and-is frictionally engaged with plate 2 2 I 'by means :of bolt 232. :Byreleasing: bolt 232 an'd=1noving plate 22! with respeet to stationarycam .12 Matheposh tion of the movable camfidii can-bewariedwith respect to the-stationary cam 21 4 :tolengthenror shorten the depressed portion :provided :by -.the two cams, the cams having thesa-merconfiguration. If thecamsare placed so: that thamovable cam is identicallypositioned relative tothefixed am, then -the maximum driving period :of .sprocketi2 ll3 is. provided. As. cam :22 2.5 :is rotated clockwise in figure .6, the 'lengthof i the driving period is shortened: in Figure 16,1 cam 22 51 has: been rotated slightlyrwithrespect to ,camz2 Hits, shorten the :efiectivelength of the depressed;camportion andrso shorten z-the .drive period. iThe .cam :fol-

lower 52 t2 lisof ;:such.:a widthzthatdtlmlls over both'cams s01 thatathe length of thedriving period :ofwsprocket Zdfinambe varied to the; requlsiteex- 1tent,;ascwillzbegexplained.

Figures 3-and 9=is-usefu1 on all-blanks; that drive J shown in Figures 9, 10 and 11 isparticularly-suited to the feeding of blanksinsuccession from a stack when the blanks are made of such a stock that they have a tendency to warp. In this form, two positive feed wheels [Bil-a are :mounted on shaft I83 beyond the fingers 15!. When fingers [51 rock clockwise (Figure 9), the blank adjacent the feed .wheels is released toiengage the feed wheels. When the fingers are rocked counterclockwise, they supportthe next foremost blank-sealing that blank against release while the releasedblankis against .the wheels 184-11 :for positive feed ng.

Tosupportthe stack of blanks witha minimum of friction along theirsupported edgesa rod 29l is extended betweenthe frame members ,IZ I-and slidable brackets l 16 are mounted thereon tosupport adjustably rods Iii-which provideithestack support. The .end of each Zrod ll? .is suitably formed and is spaced from .the peripherytof the cooperating wheels lBfi-a sothat aspaceofcontrolled width is provided between each wheeland each rod end for passage of the foremostblank. The space between the wheels andthe rods H1 is slightly more than the thickness of a blank-so that a released-blank can slide betweenithe rod ends and the wheel. :In addition, the ends of-rods ll! are provided at a suitable angle to a;t a ngent to the wheel surface opposite ,to the rods. .We have found this angle to be fairly critical; it should be between about 3 and about 15f, although weprefcr an angle of 5. If theangleis too great, the rod endstear the blank; .if the angle is too small or if-the ends areparallel;to,the tangent, then too much'friction ispresent.

To assist in release of theforemost blank,,stripping members H8 are adjust ably mounted .in brackets i'i9 on rod 29!, thestrippin zmembers extending partially over the ends of-the fingers 'l5l so that, while the finger-scan support the foremost blank, the blank is stripped off the fingerswhen the fingers are rocked to,blank release position.

The positive feed of ,a .z eleased blank 'Means are provided for feeding a released blank positively to the plunger and die mechanism, when the blank is released from the wheel i 84 and its associated drive mechanism. This meansineludes guide members 241 lFigure .3) having suitable guide rollers 242 (FigurelQ) thereon-and adjustably mounted on support frames -=2'H. Rubber belts2 l3 (Figures '3, 5 and 9) are trained about pulleys 25 i supportedon a stub shaft:246 on frames 21i and over idler pulleys 241, the belts moving downwardly over the adjustably supported members '24! to move a blank down and into engagement with transverse stops :35] in the die-fl i. Belts 245 are driven by pulleys 248 slidably carried upon a shaft 259, the shaft being extended-between suitable journals 25! mounted uponthe end ofarms 252.

The arms 252 are pivotally-mounted upon a shaft 253i on opposite sidesof the machine so that the weight of shaft 2- 59, pulleys 243 and arms 252 serves to maintain a tension upon the belts.

carried onthe'end thereof, a chain 2-32 being trained about this sprocket; and about sprocket 263 onshaft 253 (Figural). Another-sprocket 264' is provided upon shaft 2 53 and -a chain-2B6, driven bya sprocket -269-onhand wheel shaft--B3,

is extended about this sprocket and about an idler sprocket 268 mounted on a stub shaft 261 on the right-hand side frame.

The position of the belts 243 and the adjustable guides 24! are adjusted to suit the length of the blanks to be fed by sliding pulley 248 on shaft 249 and by moving the support frames 27! along angle irons 94 to which the frames are secured by stud 272, plate 273 and nut 214. The guides 24| are hinged at one end on the frames as at 276 and are adjustably supported as at 211 by a connection which includes a spring 278. An arm 279 is hinged as at 281 on each frame, each arm carrying a pulley 244 and the idler 241. By moving the arms, the tension on the belts can be varied to suit.

The blank receiving station angle It is a feature of this invention that the blank receiving station provided by the face of the die 94 is at a relatively small acute angle to the vertical 29 so that when the blank is released it falls back against the die face and not toward the plunger. By moving the blank positively into engagement with stops or pins 35f, bouncing of the blank is eliminated while the angle of the die ensures that the blank, when released, falls in and rests securely against the die face so that even a blank of a relatively light paper stock is in a position of correct alignment before the plunger engages the blank and faces it on into the die. If the die face is too nearly vertical, the blank may fall toward the plunger while, if it is too acute, the blank may slip against the plunger. In the device shown in the drawings, an angle of 18 is employed. This has been quite satisfactory; an acute angle between 3 and 25 suffices and preferably between 5 and 18.

By varying the adjustment of the speed change device 45 by rotating crank handle 53, the rate of feed and of assembly can be varied instantly to that desired. This enables the production of the described machine to be coordinated with the demand rate, for example, of a container filling machine.

We claim:

1. A mechanism for feeding blanks of sheet material singly and in predetermined timed relationship, the mechanism comprising a magazine having an inclined blank supporting member having a surface for supporting blanks on edge on said surface; a feed roller having a friction surface, said feed roller being mounted at the lower end of said magazine, its friction surface being spaced less than double the blank thickness from the edge of said supporting surface to provide a feed gap therebetween permitting only single blanks to pass between said supporting member and roller; a stop member underneath said feed gap opposite said feed roller and movable towards, and away from, said roller into and out of the path of the blanks; said stop member being separate and apart from said roller; and drive means for intermittently driving said roller and for moving said stop member into and out of said path in predetermined timed relationship with respect to the rotation of said roller.

2. The structure claimed in claim 1 in which, in addition, means are provided for vibrating said blank supporting surface.

3. A mechanism for feeding blanks of sheet material singly and in predetermined timed relationship, the mechanism comprising, a magazine having an inclined blank supporting member having a surface for supporting blanks on edge on said surface; a main feed roller having a friction surface, said main feed roller being mounted at the lower end of said magazine, its friction surface being spaced less than double the blank thickness from the edge of said supporting surface to provide a feed gap therebetween permitting only single blanks to pass through said gap; an upper feed roller having its axis above the axis of the main roller for engaging above the main roller the frontmost blank of a stack of blanks placed in said magazine; a stop member underneath said feed gap opposite said main roller and movable towards, and away from, said main roller into and out of the path of the blanks fed through said gap; said stop member being separate and apart from said rollers; and drive means for intermittently driving said main and upper feed rollers and for moving said stop member into and out of said path in timed relationship with respect to the rotation of said rollers, the arrangement of the main and upper feed follers being such that the frontmost blank extends at an angle between 3 and 15 degrees with respect to the tangent at the main roller at said p- 4. A mechanism for feeding blanks of sheet material singly and in predetermined timed relationship, the mechanism comprising, a magazine including an inclined blank supporting member having a surface for supporting blanks on edge on said surface; a feed roller having a friction surface, said feed roller being mounted adjacent the lower end of the magazine; means for adjusting the end edge of said blank supporting member with respect to said feed roller to provide a feed gap of adjustable thickness between the edge of said blank supporting member and said roller surface; a stop member underneath said feed gap and opposite said roller, said stop member being separate and apart from said roller and movable towards, and away from, said roller into and out of the path of blanks passing through said gap; a stripper element opposite said roller underneath said feed gap for engaging blanks during motion of the stop member out of said path and stripping blanks off said stop member during said motion; and drive means for intermittently driving said roller and for moving said stop member into and out of said path in predetermined timed relationship with respect to the rotation of said roller.

5. The structure claimed in claim 4 in which the inclined blank supporting member comprises two spaced blank supporting bars, and in which further two spaced feed rollers are provided instead of a single feed roller, one feed roller being adjacent the lower end of each bar.

EDWARD J. PAGENDARM.

References Cited in the file of this patent UNITED STATES PATENTS Number 

